Pump



July 3, 1951 D. o. MANSEAU PUMP 2 Sheets-Sheet 1 Filed Aug. 12, 1946 July 3, 1951 D. o. MA-NSEAU PUMP 2 Sheets-Sheet 2 Filed Aug. 12, 1946 Patented July 3, 1951 UNITED STATES rare OFFICE 2,559,255 PUMP David O. Manseau, Berkley, Mich.

Application August 12, 1946, Serial No. 689,950 9 Claims. (01. 103-133) This invention relates to pumps and more particularly to an improved positive displacement rotary pump which may be used as a forcing pump or a compressor, as well as a lifting pump or a vacuum pump. The present application is a continuation-in-part of my cd-pendirig appli-' cation Serial No. 676,626, filed June 14, 1946, now U. s. Patent No. 2,489,041. Reference is also made to my applications Ser. No. 549,328, filed August 14, 194 Serial No, 568,252, filed December- 15, 1944; Serial No. 571,472, filed January 5, 1945; which applications are now abandoned. 7

One of the objects of the present invention is to provide an improved lightweight positive displacement pump adapted for various applications such for instance as for compressing gaseous refrigerant in refrigerators of varioustypes; for circulating cutting fluid in machine tools; for sup plying lubricant, under pressure if desired, to various parts of machines; for creating hydraulic pressure and operating various devices, suchfor instance as motor vehicle brakes; for lifting liq uids; creating vacuums; and for other like applications. v

Another object of the present inventionis to provide an improved positive displacement pump in which greatly objectionable pulsations of dis charge are overcome and largely eliminated and nearly steady Or uniform discharge is produced. Pulsating discharges, particularly in pumping liquids, produce considerable momentum effects in the supply and delivery columns, with resulting high pulsating stresses and rough operation'of the pump itself as well as of the connected hydraulically actuated'devices. 7

Still another object of the invention is to provide a pump of the foregoing character in which pump the parasitic o ineffective space is greatly decreased and, consequently, the efiiciency of the pump is-increased.

A further object of the invention is to provide a pump of the foregoing character which is com pact in design, has its mass arranged more concentrically, has less moving parts, is more bal anced in operation and operates more smoothly with less friction, heat and wear, requires less lubrication, and produces less noise. H

A still further object of the present invention is to provide an improved pump of the foregoing character, which pump is flexible in its capacity,

i. e. the output of which can be varied within wide limits, and particularly by varying the speedof the pump.

A still further object of the invention eraro Vide' an" improved pump of" theforegoingcharacter the capacity of which for a given speed may be changed by changing only a few relatively inexpensive parts of the pump. H

A still further object of the invention is to provide an improved rotary positive displacement pump in which the ratio of the moment of inertia of the unbalanced mass to the capacity of the pump is greatly reduced.

A still further object of the invention isto provide a pump of the foregoing character which has a reduced number of parts, which parts are of simple geometric forms, do not include elements' of curves requiring complicated machining set-ups and are capable of precision machining by relatively inexpensive means and methods.

A still further object of the invention is to pro- Vide a pump of the foregoing character, having: a construction permitting use of materials and heat treatment processes from a wider range of selection.

A still further object of the invention is to provide an improved rotary positive displacement pump in which sliding of the constrained surfaces under load is reduced and substantially rolling contact is used, and in which the contact surfaces'are'advantageously prepared for the particmar type of contact, thereby greatly decreasing friction and wear of the vital parts of the pump and prolonging its life. I

A still further object of the invention is to provide" an improved positive displacement pum of thefor'egoing character which is relatively inexpensive to'make and is easy to service and repair.

It is an added object of the presentinvention to provide an improved rotary positive displacement pumpwhich is simple and rugged in construction, dependable in operation, and which once properly installed and adjusted can operate for a' number of years without requiring special attention and care. In installations such as domestic refrigerators and the like, this feature is of critical importance;

Other objects of this invention will appearlin the following description and appended claims, reference being had to the accompanying drawing's'for'mirig a part of this specification, wherein like" reference character designate corresponding parts in the several views.

Fig. 1 shows my improved pump in longitudinal vertical section. 4 v v V Fig. 2'is a side View, and Fig; 3 is a top view of the cone member of the pump. Fig. li's' a' side v iew, and Fig. 5 is an end view oftl iedividing'plate o f'thep'u'mpQ I n 1 Fig. 6 is" an and view'of the'purnp of rig. 1', the

3 observer being presumed to look from left to right.

Fig. '7 is a sectional view taken in the direction of the arrows on the section plane passing through the line 1-1 of Fig. 1.

Fig. 8 is a top view of the valve plate of the p mp- 7 Fig. 9 is a side view and Fig. 10 is an end view of the valve plate of Fig. 8, both of said figures showing the valve plate in section.

Before explaining in detail the present invention it is to be understood that the invention is not limited in its application to the details of con-- struction and arrangement of parts illustrated in the accompanying drawings, since the invention is capable of other embodiments and of bein practiced or carried out in various ways. Also it is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation.

V In the drawings, there is shown by way of example a pump embodying the present invention. The drawings illustrate a gas pump or compressor particularly, but not exclusively, adapted for compressing gaseous refrigerant in refrigerators of domestic type. It will be understood, however, that the invention is not limited to such an application and that it is applicable to pumps of other types as well as to pumps intended for other ap= plications.

Referring to the drawings, the pump comprises, generally, a member having a conical contact surface and a member having a complementary surface adapted to form a fluid-tight line contact with said conical surface, said members having a predetermined space between said surfaces. The first of said members if exemplifled in the present embodiment of the invention by a stationary cone member generally designated by the numeral 50, said member comprising a cylindrical portion H and a portion [2 preferably integral with portion H and forming a part or element of a sphere, the center C of which lies on the axis of the cylindrical portion H. The radius of the portion i2 is greater than that of the cylindric portion H. The portion I2 is prvided with a right conical surface I3, the vertex of which coincides at point C with the center of the spherical portion l2. The directrix M of the conical surface 13 is, thus, a line of intersection of the spherical and conical surfaces. The member It is provided with a straight slot disposed in a diametrical plane and cutting through the spherical portion i2 and part of the cylindrical portion H, as is best shown in Figs. 2 and 3, to

receive the half-circular dividing plate it. The 7 plate It has formed on it or secured to it in any suitable manner a ball ll concentric with the plate and adapted to fit in part into a socket or spherical recess I8 provided in the member It,

the center of the recess l8 coinciding at point C with the vertex of the conical surface [3, and therefore with the center of the spherical portion symmetrically disposed conduits 20, 2|, 22 and 23 are provided in the member I!) having ports in the conical surface l3, immediately adjacent the slot 15, as well as in the bottom of the cylindrical portion H. V

The complementary surface cooperating with the conical surface I3 is thestraight plane surface 25 provided on the face of a flange member 26 disposed to have said'surface 25 in a fluidtight line contact with the conical surface [3. in the center of the circular flange of said member 26 there is provided a semi-spherical socket 21 adapted to receive a portion of the ball ll of the dividing plate Hi.

It will now be understood in view of the foregoing that with the members it and 26 in operative contact, their axes intersect each other at the point C, which point at the same time constitutes the theoretical vertex of the conical surface l3, and the center of the ball ll. It should be understood that the ball ll should not be so oversize and should not fit in its sockets so tightly as to interfere with the fluid-tightness of the line contact of the surfaces 53 and 25.

In accordance with the invention, improved means are provided to confine or sealthe space formed between the members is and 25, and indicated in Fig. 2 by the numeral 363. Said means are exemplified by the socket 3! detachably secured in any suitable manner, such as with the aid of screws 32, to the peripheral edges of the member 26 overhanding the spherical portion [2 of the cone member iii. The socket 3| has an internal bearing surface forming a portion or element of a sphere having its center at the point C, its radius being equal to that of the spherical portion [2 of the member It plus'necessary clearance for sliding fluid-tight lubricated fit. The width of the socket member 3! is selected to ensure that it embraces enough of the spherical surface l2 to ensure sealing of the space 39 in all operative positions of the members It and 25.

The socket 3i receives and retains in place the dividing plate 55, the circular edges of which are fitted to the spherical surface of the socket for fluid-tight contact but permit slight sidewise sliding motion therein. The straight or diametrical edge iii of the plate It is fitted to the straight surface 25 for fluid-tight contact therewith, but permits the slight rocking of the straight surface on the edge by being rounded as is best shown in Figs. 4 and 5.

The included angle of the conical surface [3 is, in the present embodiment of the invention equal to approximately 169, which angle represents a satisfactory angle for average conditions. However, other angles may be used under specific conditions, such as for relatively high speeds of operation, as explained later. Apart from considerations of speed, selection of the angle of the cone and of the length of the generatrix thereof is governed substantially by the same consideration as the selection of the length of the stroke and the area of the piston in a reciprocating pump.

The member as is actuated to cause the line of contact of the surfaces It and 25 to progress or rotate around the vertex of the cone. In the process of such a motion, the axis Of the member 26 moves to define or generate a cone having vertex at the point C, with its included angle being equal to minus, the included angle of the conical surface 53. Such motion of the member is effected with the aid of a shaft 35 co-axial with the cone member In and journalled in a long bearing 35 provided in the housing it. The shaft 35 has a crank 31 engaging the member 25 at a cylindrical bore into which it is fitted for running lubricated fit. The coinciding axes of the bore and the crank 3! are perpendicular to the surface 25 and pass through the point C. With surfaces 13. and 25 in contact, the axis of the crank 31 forms with the axis of the member It an angle equal to one-half of the angle A. k With the construction so far described, it will now be understood that as the shaft is rotated, clock-wise in the present embodiment looking at its right-hand end from right to left in Fig. 1, the member 26 will be moved to have its axis generate a cone, the included angle of which is equal to angle A, with the vertex of the cone being at point C and remaining at rest. As a result of such a motion the line of contact of the surfaces It and 25 will progress around the vertex C in the clock-wise direction. It should be understood that in the process of such a motion, the member 263 does not rotate around its own axis and that the surfaces I3 and 25 substantially roll on each other. It should be understood however that in this type of contact there is a small amount of relative movement between the contact surfaces at the line of contact. The amount of such relative movement depends on the included angle of the cone and decreases as said angle approaches 180. By the use of an included angle such as herein disclosed, the amount of such movement and resulting friction are greatly reduced as compared with other pumps. Moreover, in designing pumps embodying the present invention for high speed operation, where elimination of friction becomes of critical importance, by increasing said included angle in accordance with the invention, the friction may be substantially eliminated and a pump exceptionally advantageous for high speed operation may thus be produced. Generally, the use of cones with less than 120 included angle is undesirable if high speed operation of the pump is contemplated.

The members i i} and 26 are preferably made of steel and their contact surface hardened and polished.

Due to the above-described movement of the line of contact between the surfaces I3 and 25, the fluid contained in the space between said surfaces, with no dividing plate being provided, would be driven in front of the moving line of contact following it from behind. Because of the provision of the dividing plate It restrained from rotation, the fluid is pressed in front of the line of contact, and vacuum is created behind the same. Referring now to Fig. 3, with the line of contact indicated therein by a heavy dotted line and designated by the letter L, and the dividing plate It being in place, and the space between the surfaces I3 and 25 sealed, it can be easily seen that as the line of contact 1 moves in the direction indicated by the arrow, the fluid in the compartment formed between the line L and the lower portion (as appears in Fig. 3) of the dividing plate It is being pressed and forced under pressure into the discharge conduit 2 I, while vacuum is being created behind the line L. which will draw the fluid from the intake conduit 26 controlled by an intake valve 5 3-, and conduits 55a and. 55 provided in the cover (see Figs. 1 and 6). The fluid will then flow into the conduit from the intake port provided in the housing 4%, through the chamber or space formed in the housing 40, through a filter 51, dampening chamber 58 and pipe 59 connected to the cover 50, in registry with the conduit 55 thereof, by means of a suitable coupling, such as The fluid under pressure will be discharged through the conduit 2| controlled by the discharge check valve 6!, discharge conduit 52 provided in the cover 50, and into a discharge pipe 53 connected to the cover Ed, in registry with the conduit 62, by means of a coupling 64.

In the position of the line of contact L shown in Fig. 3, the space between the surfaces I3 and 25 on the opposite side of the slot I5 or dividing plate I6, or on left-hand side in Fig. 3 and indicated there by the numeral N, has reached its maximum volume and is at the end of its suction phase. As the line L moves from the position indicated, the space N begins to diminish in volume, compressing the fluid contained therein, closing the intake check valve 65 controlling the intake conduit 22 and opening the discharge check valve es controlling the discharge conduit 23. Therefore the fluid begins flowing through the discharge conduit 23 and will continue to discharge it until the line L passes over the port of the discharge conduit 23, i. e. moves through the angle of substantially 270.

It should also be understood that as the line L has moved through the angle of slightly over from the position shown in Fig. 3, and crosses the port of the intake conduit 22, the vacuum space is created behind said line L, which space will grow in volume from nearly zero to the maximum volume when the line L again reaches the position shown in Fig, 3. Thus, the discharges from the discharge conduits 2i and 23 of my pump continue, respectively, for 270 of the rotation of the line of contact, and of the shaft 35, and overlap each other at their beginnings and ends for 90 of the rotation of said line and the shaft. For instance, the period of movement of the line L for the first 90 from its position in Fig. 3, said period will be the last 90 of discharge of fluid through the conduit 2i and the first 90 of discharge through the conduit 23. If the volumes of such discharges are plotted in a rectangular system of coordinates against the degrees of rotation of the shaft, they will be represented by curves rising from zero to maximum and dropping back to zero, and overlapping each other at their beginnings and the ends (1. e. zero points) for 90. The combined or resulting discharge curve will, therefore, appear as a line with very small fluctuations and disposed substantially along the points of maximum discharges of separate ports. In the above discussion the effect of the discharge and intake ports, which modifies somewhat the above values, has been neglected for the sake of clarity of explanation.

It can now be understood, that such operation of my improved pump produces substantially non-pulsating, even discharge, and consequently smooth operation of the pump. Such operation has a number of very important advantages well appreciated by those skilled the art both from the standpoint of the pump operation and its operation stresses as well as from the stand point of application of the dis-charge. Exprcssed in the language of the art, the discharge of my improved pump approximates uniform or straight line discharge. Moreover, the discharge, in addition to being nearly is substantially equal to the momentary maximum discharge produceable by eith r of the discharge ports, and at no time it drops to 0. Thus my improved pump delivers more fluid per one revolution of the shaft than other pumps of this general nature and having contacting surface members of the same size but different organization of operative parts.

It should also be understood that the intake characteristics of my improved pump are similar to the above described discharge characteristics. Namely the intakes from the conduits 20 and 22 continue for 270 of the shaft rotation and overlap each other at their beginnings and the ends for 90 of the shaft rotation.

The substantially uniform suction and discharge characteristics of my improved pump present a substantially uniform driving resistance which is more advantageous for the driving machine or motor than intermittent resistance and it prolongs the life of such machines or motor.

The reciprocating movement of points on the member 25 is utilized 'to operate with the aid of a connecting rod it universally connected to the member 26 as at 'i I, a reciprocating oil pump 72 provided in the bracket 53 secured within the housing 4?], and pumping oil into a tank 94. It should be understood that the connection ll should take care of the wobbling movement of the member 2%. From the tank as the oil is sprayed through a number of holes such as 15 on the operating parts of the pump. Oil-carrying conduits I8 and T. supply oil to the ball I! and the crank pin 3'1. A groove is provided on the shaft lubricates the bearing 36. A seal generally indicated by the numeral 89 is provided to prevent leakage of oil at the end of the shaft 35 and of the pumped fluid. The return oil conduit 8| leads the oil from the bearing 36 into the lower part of the housing id. The level of oil in the housing 4&3 is maintained approximately at the height of the top of the cone member Hi to ensure sufiicient supply of oil and to lubricate the spherical surface l2.

.It should be particularly appreciated that in my improved pump both the amount of unbalanced mass and location of its center of gravity from its axis of gyration are greatly reduced, thus improving the static balance as well as the dynamic balance of the pump. Expressed in the form of a ratio of the moment of inertia of the unbalanced mass to the capacity of the pump at a given speed, such ratio for my improved pump is exceptionally low. It should be appreciated in this connection, that since moment of inertia of a revolving or an oscillating mass is determined not only by the magnitude of such mass but also by the square of the radius of its gyration, merely decreasing the unbalance mass may not be appreciably beneficial and, in fact, it may be detrimental to the balance of the pump if it mustbe achieved by moving such unbalanced mass, even decreased in its amount or quantity, further away from the axis of its movement.

It can also be appreciated that since due to its improved dynamic balance, my improved pump may be operated at relatively high speeds (speed at 4,200 R. P. M. havingbeen already successfully used), and since its speed may be varied selectively through a wide range, the capacityof my pump is extremely flexible and may be widely varied. This feature is extremely important, since in many installations the most advantageouspump capacity can be selected by an actual trial after the pump has been installed, and effected merely by changing the gearing or pulleys.

By virtue of the above-described construction the objects of the invention, listed above, and numerous additional advantages are attained.

I claim:

1. In a pump, a rigid member having a conical contact surface and a rigid member having a straight contact surface, said members being operatively mounted to have their contact surfaces in a line contact, means to actuate one of said members to cause said line of contact to move continuously around the vertex of the conical surface, means confining the space between said members, rigid means carried by said actuated member and dividing said confined space into two chambers, said members being adapted to discharge the fluid from each of said chambers for substantially 270 of the rotation of said line of contact out of each 360 angular movement thereof with the discharge periods of said two chambers overlapping each other at their beginnings and ends for substantially of the rotation of the line of contact of said surfaces.

2. In a pump, a rigid member having a conical contact surface and a rigid member havin a'straight contact surface, said members being operatively mounted to have their contact surfaces in a line contact, means to actuate one of said members to cause said line of contact to move continuously around the vertex of the conical surface, means confining the space between said chambers, rigid means carried by said actuated member and dividing said confined space into two chambers, said members being adapted to draw the fluid into each of said chambers during the motion of said line of contact through the angle of substantially 270, with the intake periods of said two chambers overlapping each other at their beginnings and ends for substantiaily 90 of the rotation of the line of contact of said surfaces, said members being adapted to draw the fluid into each of said chambers and to discharge it therefrom, the intake and the discharge periods from the two chambers overlapping each other, respectively, and means combining respectively the intakes and the discharges of both of said chambers.

3. In a pump, a rigid member having a conical contact surface and a rigid member having a straight contact surface, said members being operatively mounted to have their contact surfaces in a line contact, means to actuate one of said members to cause said line of contact to move continuously around the vertex of the conical surface, means confining the space between said chambers, metal plate carried by said actuated member and dividing said confined space into two chambers, said members being adapted to draw the fiuid into each of said chambers during the motion of said line of contact through the angle of substantially 270, with the intake periods of said two chambers overlapping each other at their beginnings and ends for substantially 90 of the rotation of the line of contact of said surfaces, said members, bein adapted to draw the fluid into each of said chambers and to discharge it therefrom, the intake and the discharge periods from the two chambers overlapping each other, respectively, for substantially 90 of the movement of the line of contact of said surfaces.

4. In a pump, a metal member forming in part a portion of a sphere and having a conical contact surface with the vertex coinciding with the center of the sphere, a metal straight surface member operatively mounted to have its straight surface in a line contact with said conical surface along the generatrix thereof, a socket member carried by said straight surface member, said socket member having internal spherical surface embracing the spherical portion of said conical surface member and adapted to confine the space between said contact surface members in all operative positions thereof, and means actuating said straight surface member to cause the line contact of said surfaces to move around the vertex of the conical surface.

5. In a pump, a metal member forming in part a portion of a sphere and having a conical contact surface with the vertex coinciding with the center of the sphere, a metal straight surface member operatively mounted to have its straight surface in a line contact with said conical surface along the generatrix thereof, a socket member carried by said straight surface member, said socket member having internal spherical surface embracing the spherical portion of said conical surface member and adapted to confine the space between said contact surface members in all operative positions thereof, means actuating said straight surface member to cause the line contact of said surfaces to move around the vertex of the conical surface and spring means acting on said straight surface member to press it against said conical surface member.

6. In a pump, a member forming in part a portion of a sphere and having a conical contact surface with the vertex coinciding with the center of the sphere, a straight surface member operatively mounted to have its straight surface in a line contact with said conical surface along the generatrix thereof, a socket member carried by said straight surface member, said socket member having internal spherical surface embracing the spherical portion of said conical surface member and adapted to confine the space between said contact surface members in all operative positions thereof, and means actuating said straight surface member to cause the line contact of said surfaces to move around the ver tex of the conical surface, and plate means carried by the straight surface member and em braced at least in part by said socket member, said plate means adapted to separate said con fined space into two parts along a fixed plane passing through the vertex of the conical surface.

7. In a pump, a member forming in part a portion of a sphere and having a conical contact surface with the vertex coinciding with the center of the sphere, a straight surface member operatively mounted to have its straight surface in a line contact with said conical surface along the generatrix thereof, a socket member carried by said straight surface member, said socket member having internal spherical surface embracing the spherical portion of said conical surface member and adapted to confined the space between said contact surface members in all operative positions thereof, and means actuating 10 said straight surface member to cause the line contact of said. surface to move around the vertex of the conical-surface, and plate means carried by the straight surface member and embraced at least in part by said socket member, said plate means adapted to separate said confined space into two parts along a fixed plane passing through the vertex of the conical sur face, and intake and delivery conduits provided in said conical surface member and communicat ing with each of said two parts of the confined space, and valve means controlling said conduits.

8. A construction as defined by the preceding claim 7, with said valve means being operatively mounted on a removable plate.

9. A compressor pump comprising means forming a part-spherical chamber, a stationary member having a conical surface forming one wall of said chamber, an abutment oscillatable in a diametrical slot in said stationary member, a member internally part-spherical and having a plane surface contacting said conical surface in line contact, said part-spherical member being mounted for gyration about the apex of said conical surface and controlling the oscillation of said abutment and cooperating therewith and with said conical surface to form pressure and suction chambers, said slot being formed with inlet and outlet ports communicating with said chambers at opposite sides of said abutment.

DAVID O. MANSEAU.

REFERENCES CITED The following references are of record in the file of this patent:

UN IT'ED STATES PATENTS Number Name Date 591,522 Artemkin Oct. 12, 1897 958,408 Kadow May 17, 1910 2,015,826 Vincent Oct. 1, 1935 2,101,051 Cuny Dec. 7, 1937 2,205,919 Brouse June 25, 1940 2,375,923 Johnson May 15, 1945 2,489,041 Manseau Nov. 22, 1949 2,496,668 Manseau Feb. 7, 1950 FOREIGN PATENTS Number Country Date 26,930 Great Britain July 16, 1914 302,495 Great Britain Dec. 20, 1928 485,660 Great Britain May 24, 1938 522,845 Germany Mar. 26, 1931 

